EP1238759B1 - Marteau - Google Patents

Marteau Download PDF

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Publication number
EP1238759B1
EP1238759B1 EP02251438A EP02251438A EP1238759B1 EP 1238759 B1 EP1238759 B1 EP 1238759B1 EP 02251438 A EP02251438 A EP 02251438A EP 02251438 A EP02251438 A EP 02251438A EP 1238759 B1 EP1238759 B1 EP 1238759B1
Authority
EP
European Patent Office
Prior art keywords
beatpiece
sleeve
spindle
rearward
ram
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02251438A
Other languages
German (de)
English (en)
Other versions
EP1238759A1 (fr
Inventor
Andreas Hanke
Achim Buchholz
Ralf Bernhart
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Black and Decker Inc
Original Assignee
Black and Decker Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from GBGB0105547.4A external-priority patent/GB0105547D0/en
Priority claimed from GBGB0125749.2A external-priority patent/GB0125749D0/en
Application filed by Black and Decker Inc filed Critical Black and Decker Inc
Publication of EP1238759A1 publication Critical patent/EP1238759A1/fr
Application granted granted Critical
Publication of EP1238759B1 publication Critical patent/EP1238759B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/24—Damping the reaction force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/062—Means for driving the impulse member comprising a wobbling mechanism, swash plate
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/08—Means for retaining and guiding the tool bit, e.g. chucks allowing axial oscillation of the tool bit
    • B25D17/084—Rotating chucks or sockets
    • B25D17/088—Rotating chucks or sockets with radial movable locking elements co-operating with bit shafts specially adapted therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/20—Devices for cleaning or cooling tool or work
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0057—Details related to cleaning or cooling the tool or workpiece
    • B25D2217/0065—Use of dust covers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/191—Ram catchers for stopping the ram when entering idling mode
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/365—Use of seals

Definitions

  • This invention relates to electric hammers as described in the preamble of claim 1. Such electric hammers are known from document DE-A-19621610.
  • Such hammers will normally have a housing and a hollow cylindrical spindle mounted in the housing.
  • the spindle allows insertion of the shank of a tool or bit, for example a drill bit or a chisel bit, into the front end thereof so that it is retained in the front end of the spindle with a degree of axial movement.
  • the spindle may be a single cylindrical part or may be made of two or more cylindrical parts, which together form the hammer spindle.
  • a front part of the spindle may be formed as a separate tool holder body for retaining the tool or bit.
  • the hammer is normally provided with an impact mechanism comprising a motor that drives a piston, which may be a hollow piston, to reciprocate within the spindle.
  • the piston reciprocatingly drives a ram by means of an air cushion located between the piston and the ram.
  • the impacts from the ram are transmitted to the tool or bit of the hammer via a beatpiece located within the spindle.
  • Some hammers can be employed in combination impact and drilling mode in which the spindle, or a forwardmost part of the spindle, and hence the bit inserted therein, will be caused to rotate at the same time as the bit is struck by the beat piece.
  • the forward end of a tool or bit When the hammer is to be used the forward end of a tool or bit is pressed against a workpiece, which urges the tool or bit rearwardly within the hammer spindle. The tool or bit in turn urges the beatpiece rearwardly into its operating position in which the rearward end of the beatpiece is located within the reciprocating path of the ram. In the operating position the beatpiece receives repeated impacts from the ram.
  • the forward impact from the ram is transmitted through the beatpiece to the bit or tool and through the bit or tool to the workpiece.
  • a reflected impact is reflected from the workpiece and is transmitted through the bit or tool to the beatpiece. This reflected, or reverse impact must be absorbed within the structure of the hammer in such a way that the reverse impacts do not over time destroy the hammer and so that the reverse impacts are not transmitted to the end user.
  • the next forward impact of the ram on the beatpiece urges the beatpiece forwardly into its idle mode position.
  • the beatpiece can move forwardly and stay forwardly because the tool or bit is no longer urging it rearwardly, because the tool or bit also assumes a forward idle mode position.
  • the ram also moves into a forward idle mode position. In the idle mode position of the ram, the air cushion is vented and so any further reciprocation of the piston has no effect on the ram. This forward movement of the components on entry into idle mode generates the greatest impact forces on the structure of the hammer, in particular on the hammer spindle.
  • the number of idle strikes ie. the number of reciprocations of the ram, beatpiece and tool or bit, when the bit or tool is removed from the workpiece need to be minimised in order to minimise the number of high impact force idle strikes that have to be absorbed by the structure of the hammer.
  • This is generally achieved by catching the ram and/or the beatpiece in their idle mode positions so that they cannot slip rearwardly to cause the ram to move into a position in which the air cushion is closed and the ram and thus the beatpiece begin to reciprocate again.
  • the beatpiece In order for the maximum impact to be transmitted from the ram to the tool or bit, via the beatpiece, the beatpiece must be co-axial with the spindle. Thus, high efficiency is achieved if the reciprocating movement of the beatpiece within the spindle is guided to ensure good axial alignment with the axis of the spindle.
  • the arrangement in US4,476,941 has a complicated multi-part spindle arrangement with a first sleeve for guiding a rearward reduced diameter portion of the beatpiece, which sleeve extends from the inside to the outside of the spindle, between two spindle parts.
  • the impact of the beatpiece on entry into idle mode is absorbed by a second sleeve, located forward of the first and within a different one of the spindle parts.
  • the second sleeve also guides a forward increased diameter portion of the beatpiece.
  • the arrangement in US4,476,941 has a problem with dust ingress, in particular during periods when a tool or bit is removed from the tool holder of the hammer, into the portion of the forward sleeve where the beatpiece is guided.
  • DE196 21 610 overcomes some of the problems discussed above, but still has the disadvantage of a relatively complex three part spindle arrangement, having sleeves for beatpiece guiding mounted and guided in different spindle parts. Again the usual tolerance issues between spindle parts can reduce the accuracy with which the beatpiece is guided and complicates the sealing of dust from the inside of the spindle. Again the design in DE196 21 610 has a complicated multi-part spindle, beatpiece guiding and damping structure, with the associated assembly problems and cost implications.
  • the present invention aims to provide a beatpiece guiding and damping arrangement which solves all of the problems discussed and which results in a relatively simple and easy to assemble structure.
  • the sleeve arrangement according to the present invention enables easy assembly of the sleeves and beatpiece and associated components, as a sub-assembly, within a single spindle component part. It also enables simple sealing of the inside of the spindle from dust, as the sleeve arrangement itself forms an effective barrier to dust ingress.
  • the sleeve arrangement facilitates a reduction in the intensity of impacts on the structure of the hammer on entry into idle mode and catching of the ram and beatpiece in idle mode. On entry into idle mode, the increased diameter portion of the beatpiece hits the forward sleeve and imparts forward momentum to the forward sleeve and itself moves rearwardly, but with relatively low momentum thus facilitating catching of the beatpiece and/or ram.
  • the two part sleeve arrangement enables additional advantages to be achieved in an easy to assemble sub-assembly.
  • annular seal can be located between the beatpiece and said one piece spindle part, in front of the sleeve arrangement.
  • annular seal can be located between the beatpiece and the forward end of the forward sleeve, and this seal may be recessed within the forward end of the forward sleeve. In this way the beatpiece is guided within the sleeve arrangement in a dust free region of the spindle.
  • annular seal can be located between the forward sleeve and said one piece spindle part.
  • the sleeve arrangement can be arranged to enclose the mid-portion of the beatpiece to form a self-contained sub-assembly, which is assembled into said one piece spindle part. This provides a simple assembly procedure.
  • the mass of the front sleeve preferably is less than or equal to the mass of the beatpiece. In a preferred embodiment the mass of the front sleeve is less than half of the mass of the beatpiece.
  • the beatpiece has a second increased diameter portion, rearward of the first, which second portion is engageable with a resilient beatpiece catching ring.
  • the ring is mounted preferably within the rearward sleeve and is arranged to catch the beatpiece in a forward position in idle mode, by limiting the rearward movement of the second increased diameter portion during idle mode.
  • the inclusion of the beatpiece catching arrangement in the sleeve arrangement again simplifies assembly as the beatpiece catching ring can be preassembled in a sleeve arrangement sub-assembly, which sub-assembly is then assembled into said one piece spindle part.
  • An annular gap is formed between the peripheral surface of the increased external diameter portion of the beatpiece and increased internal diameter portion of the sleeve arrangement.
  • a metal beatpiece impact ring is mounted in the rearward sleeve behind the rearward facing surface of the increased diameter portion of the beatpiece for absorbing reverse impacts from the beatpiece and transmitting the impacts to the rearward sleeve during normal use of the hammer.
  • This enables efficient transmission of reverse impacts from the beatpiece during normal operation of the hammer.
  • the impact ring can be assembled into a sleeve arrangement sub-assembly, before assembly of the sub-assembly into said one piece spindle part, thus facilitating efficient assembly procedures.
  • a damping ring may be mounted in the rearward sleeve behind the impact ring for damping the impacts transmitted from the impact ring to the rearward sleeve.
  • the beatpiece damping ring and the beatpiece catching ring are formed by the same component.
  • a resilient O-ring is located between a rearward facing external shoulder of the rearward sleeve and a fixing for axially limiting the rearward movement of the rearward sleeve within said one piece spindle part and during normal operation of the hammer, the increased diameter portion of the beatpiece repeatedly abuts a forward facing internal shoulder of the rearward sleeve.
  • the reverse impacts are transmitted from the beatpiece to the rearward sleeve and are then damped by the O-ring before being transmitted to the spindle via the fixing.
  • the intensity of the reverse impacts from the beatpiece which are transmitted to the spindle is reduced.
  • a resilient O-ring located between a first forward facing shoulder of the forward sleeve and a first rearward facing shoulder of the spindle urges the forward sleeve into a rearward position within the spindle to open up a gap between a forward facing part of the forward sleeve and a rearward facing part of the spindle, which gap is closed by forward movement of the sleeve on entry into idle mode of the hammer.
  • the present invention enables simplification of the spindle structure and the hollow spindle may be formed as a single component.
  • the hollow spindle may be formed as two components, for example when it is desired to remove and/or rotate a forward tool holder portion of the spindle from and/or with respect to a rearward portion of the spindle.
  • a first spindle component may house the piston, ram and beatpiece and a second component may form a tool holder which is removable from the first component.
  • the hammer shown in Figure 1 comprises an electric motor (2), an intermediate gear arrangement (14, 20) and a crank drive arrangement (30-36) which are housed within a metal gear housing (not shown) surrounded by a plastic housing (4).
  • a rear handle housing incorporating a rear handle (6) and a trigger switch arrangement (8) is fitted to the rear of the housing (4).
  • a cable (not shown) extends through a cable guide and connects the motor to an external electricity supply.
  • a hollow cylindrical spindle (40) is mounted within the hammer housing.
  • a piston (38) and a ram (58) are located within the spindle.
  • the motor (2) drives a crank plate (30) via an intermediate gear arrangement (14, 20).
  • the crank-plate (30) reciprocatingly drives the piston (38) within the rearward part of the spindle (40) via a crank arm (34) and trunnion (36) arrangement, as is well known in the art.
  • An O-ring seal (42) is fitted in an annular recess formed in the periphery of the piston (38) so as to form an airtight seal between the piston (38) and the internal surface of the hollow spindle (40).
  • the armature pinion (3) rotatingly drives the intermediate gear arrangement (14) which rotatingly drives the crank drive spindle (22) via the drive gear (20).
  • the drive spindle rotatingly drives the crank plate (30) and the crank arm arrangement comprising the crank pin (32), the con-rod (34) and the trunnion pin (36) convert the rotational drive from the crank plate (30) to a reciprocating drive to the piston (38).
  • the piston (38) is reciprocatingly driven back and forth along the hollow spindle (40), when the motor (2) is actuated by depression of the trigger switch (8).
  • the ram (58) is located within the hollow spindle (40) forwardly of the piston (38) so that it can also reciprocate within the hollow spindle (40).
  • An O-ring seal (60) is located in a recess formed around the periphery of the ram (58) so as to form an airtight seal between the ram (58) and the spindle (40).
  • a closed air cushion (44) is formed between the forward face of the piston (38) and the rearward face of the ram (58).
  • the ram (58) moves forwardly, past the venting bores. This vents the air cushion and so the ram (58) is no longer reciprocatingly driven by the piston (38) in idle mode, as is well known in the art.
  • FIG 2 shows in more detail the hollow spindle (40) of the hammer of Figure 1.
  • the hollow spindle (40) is formed in two parts, a rearward part (40a) which houses the piston (38) and the ram (58) and a forward part (40b) which reduces in diameter in a stepped manner in the forward direction.
  • the rearward part (40a) of the spindle is non-rotatably mounted in the hammer.
  • the forward part (40b) of the spindle is rotatably mounted in a flange (1) which is bolted to a metal casing surrounding the rearward part of the spindle (40a).
  • a bit or tool (68) can be releasably mounted, by means of a tool holder arrangement (66) within the forward reduced diameter portion of the forward spindle part (40b) so that the bit or tool (68) can reciprocate to a limited extent within the forward spindle part.
  • a beatpiece (64) is mounted within the forward spindle part (40b) between the ram (58) and the tool or bit (68) and is supported and guided by a pair of sleeves (7, 9), which are mounted and guided within the forward spindle part (40b).
  • the tool or bit (68), beatpiece (64) and ram (58) are shown in their rearward operating position and in the lower half of Figure 2, they are shown in their forward idle mode position.
  • the ram (58) When the ram (58) is in its operating mode and is reciprocatingly driven by the piston (38) the ram repeatedly impacts the rearward end of the beatpiece (64) and the beatpiece (64) transmits these impacts to the rearward end of the bit or tool (68) as is known in the art. These impacts are then transmitted by the bit or tool (68) to the material being worked.
  • the beatpiece (64) is formed with two increased external diameter regions, a forward region (64a) and a rearward beatpiece catching region (64b).
  • a two part sleeve arrangement (7, 9) is used to guide the beatpiece (64) within the forward spindle part (40b).
  • the forward sleeve (7) is formed as a hollow cylinder and has a forward reduced internal diameter guiding portion (7a), which fits around and guides a forward reduced external diameter portion of the beatpiece (64).
  • the rearward sleeve (9) is also formed as a hollow cylinder and has a rearward reduced internal diameter guiding portion (9a) which fits around and guides a rearward reduced external diameter portion of the beatpiece (64).
  • the external peripheries of the sleeves (7, 9) have close radial tolerances with the cooperating internal surface of the forward spindle part (40b) and the two guiding portions (7a, 9a) are widely axially spaced.
  • the axial guiding of the beatpiece (64) is very accurate, so that the beatpiece (64) reciprocates with its axis co-axial with the axis of the forward spindle (40b). This greatly improves the efficiency with which impacts are transmitted by the beatpiece from the ram (58) to the tool or bit (68).
  • beatpieces It is common for beatpieces to be guided around their increased diameter regions. Guiding around the reduced diameter portion enables the beatpiece (64) to be designed to be non-pumping.
  • the forward sleeve (7) and the beatpiece (64) are dimensioned so that there is an annular gap between the outer surface of the forward increased diameter portion (64a) of the beatpiece and the inner surface of the increased diameter portion of the sleeve (7).
  • the forward sleeve (7) and the beatpiece (64) are dimensioned so that there is an annular gap between the outer surface of the forward increased diameter portion (64a) of the beatpiece and the inner surface of the increased diameter portion of the sleeve (7).
  • the rearward sleeve (9) contains a resilient beatpiece catching ring (15), which is formed with a reduced diameter portion (15a) having an internal diameter which is less than the external diameter of the rearward increased external diameter portion (64b) of the beatpiece.
  • the rearward increased diameter portion (64b) of the beatpiece can move past the beatpiece catching ring (15) if the beatpiece can apply a force great enough to deform the ring (15) sufficiently for the increased diameter portion (64b) of the beatpiece to pass over the reduced diameter portion (15a) of the beatpiece catching ring.
  • the front sleeve (7) has a mass, which is approximately 2.3 times less than the mass of the beatpiece (64).
  • a rubber O-ring (11) is located in front of a radially outwardly directed flange (7b) at the rear of the sleeve (7) and a rearwardly directed internal shoulder of the forward spindle part (40b).
  • the O-ring acts to maintain a small gap (13) between a slanting forward facing annular surface (7c) of the sleeve (7) and a slanting rearwardly facing internal shoulder of the forward spindle part (40b) during normal operation of the hammer.
  • the beatpiece On entry into idle mode (bottom half of Figure 2) as the beatpiece (64) moves into its forwardmost position.
  • the beatpiece has sufficient forward momentum to cause the beatpiece catching ring (15) to deform so that the increased diameter portion (64b) of the beatpiece can move forwardly past the reduced diameter portion (15a) of the ring (15).
  • the deformation of the ring (15) will absorb some of the forward movement of the beatpiece (64).
  • the forward increase diameter portion (64a) of the beatpiece impacts a rearward facing internal shoulder (7d) of the forward sleeve (7), thus transferring its forward momentum to the front sleeve (7).
  • the reflected momentum from the sleeve (7) causes the beatpiece (64) to then move rearwardly, but not with sufficient force for the rearward increased diameter portion (64b) of the beatpiece to move rearwardly past the beatpiece catching ring (15).
  • the front sleeve (7) on being impacted by the beatpiece (64) moves forwardly to close the gap (13) and transfers its forward momentum to the spindle part (40b).
  • the reflected momentum from the spindle part (40b) causes the sleeve (7) to move rearwardly, but not with sufficient speed to catch up with the beatpiece (64).
  • the rearward momentum from the front sleeve (7) is transferred to the rear sleeve (9).
  • the reflected momentum of the forward sleeve (7) is not transmitted to the beatpiece, which remains caught in its idle mode position by the beatpiece catching ring (15).
  • the O-ring (11) has only a marginal damping effect on the forward movement of the forward sleeve (7) and on entry into idle mode substantially all of the forward impact from the sleeve (17) is transmitted to the spindle part (40b).
  • the beatpiece On entry into idle mode the beatpiece is effectively caught in its forward idle mode position by the beatpiece catching ring (15). This means that the beatpiece (64) cannot move rearwardly to impact the ram (58), which could cause the ram to move rearwardly out of its idle mode position.
  • the ram (58) is caught in its idle mode position by a ram catching O-ring (17) which engages an increased diameter portion (58a) of the ram.
  • the ram (58) is prevented from returning to its operating position in idle mode and so potentially damaging idle mode impacts are avoided.
  • the tool or bit (68) When a user wishes to use the hammer again, the tool or bit (68) is pressed against a working surface and so the tool or bit is urged rearwardly in the spindle part (40b) to urge the beatpiece (64) rearwardly, to release it from the beatpiece catching ring (15).
  • the beatpiece (64) urges the ram (58) rearwardly and out of the ram catcher (17) to close the vents and form a closed air cushion between the piston (38) and the ram (58).
  • the piston (38) when the user actuates the trigger switch (8) of the hammer the piston (38) is reciprocatingly driven in the spindle part (40a) and the ram (58) follows the reciprocation of the piston due to the closed air cushion and hammering occurs.
  • the rearward sleeve (9) houses a metal beatpiece damping ring (48) for absorbing reflected impacts to the beatpiece (64) during operation of the hammer, which impacts are damped by the resilient beatpiece catching ring (15).
  • the damping ring (48) is located within the sleeve arrangement between the forward increased diameter portion (64a) of the beatpiece and the resilient ring (15) and absorbs the impacts transmitted to the rearward sleeve (9) in use of the hammer (top half of Figure 2).
  • the reflected impacts, which are transmitted from the working surface, via the tool (68) to the beatpiece (64) are damped by the resilient ring (15) before they are transmitted to the rearward sleeve (9).
  • the damped rearwardly directed impacts from the beatpiece (64) are transmitted via the connecting part (5) to the rear spindle part (40a).
  • the two part sleeve arrangement (7, 9) has a seal (21) located forwardly of it for sealing around between beatpiece (64) and the forward spindle part (40b). This seals around the beatpiece against dust entering the part of the spindle (40a, 40b) behind the seal (21) and against grease leaving the part of the spindle behind the seal (21). As the seal (21) is located forwardly of the sleeve arrangement (7, 9) the guiding of the beatpiece (64) using guiding portions (7a, 9a) is done entirely within the grease filled region of the spindle part (40b).
  • the sleeve (7, 9), O-ring (11), damper (48) and beatpiece catching ring (15) fill the space between the beatpiece (64) and the spindle part (40b) and so provides a physical barrier to the ingress of dust.
  • the sleeves (7, 9) are mounted within the spindle part (40b) with close tolerances between the external surfaces of the sleeves and the internal surface of the spindle. However, the sleeves (7, 9) are mounted so as to be able to have a limited axial movement within the spindle, as described above. Forward movement of the front sleeve (7) is limited by the resilient O-ring (11) and by the rearward facing internal shoulders of the spindle part (40b).
  • the forward end of the rearward sleeve (9) abuts the rearward end of the forward sleeve (7) and rearward movement of the rearward sleeve (9) is limited by the connecting part (5) located between the rearward end of the forward spindle part (40b) and the forward end of the rearward spindle part (40a). It can be seen that the two part sleeve design described above and shown in Figure 2 facilitates easy assembly of the beatpiece (64), sleeves (7, 9) and other associated components from the rearward end within the forward spindle part (40b).
  • Figures 3 and 4 show two different embodiments of the forward part of the spindle of a rotary hammer, with like parts to Figures 1 and 2 identified with like numerals.
  • the rotary hammer is of the type having a wobble drive to a hollow piston.
  • the hollow piston (38) reciprocates within the rearward part (40, 40a) of a one or two part spindle (40, 40a, 40b) and the ram (58) reciprocates within the hollow spindle, with the closed air cushion formed within the hollow piston, behind the ram.
  • Such hammers are known in the art.
  • the hollow spindle (40) is formed in two parts, a rearward part (40a) which houses the piston (38) and the ram (58) and a forward part (40b) which reduces in diameter in a stepped manner in the forward direction.
  • the rearward part (40a) of the spindle is rotatably mounted in the hammer.
  • the rearward end of the forward part (40b) of the spindle is mounted within the forward end of rearward part (40a) of the spindle, in a releaseable manner.
  • a bit or tool (not shown) can be releasably mounted, by means of a tool holder arrangement (66) within the forward reduced diameter portion of the forward spindle part (40b) so that the bit or tool can reciprocate to a limited extent within the forward spindle part.
  • a beatpiece (64) is mounted within the rearward spindle part (40a) between the ram (58) and the tool or bit (68) and is supported and guided by a pair of sleeves (7, 9), which are mounted and guided within the rearward spindle part (40a).
  • the sleeve arrangement is mounted within and is guided within the rearward spindle part (40a).
  • the ram (58) When the ram (58) is in its operating mode and is reciprocatingly driven by the piston (38) the ram repeatedly impacts the rearward end of the beatpiece (64) and the beatpiece (64) transmits these impacts to the rearward end of the bit or tool (68) as is known in the art. These impacts are then transmitted by the bit or tool (68) to the material being worked.
  • the beatpiece (64) is formed with one increased external diameter region (64a).
  • a two part sleeve arrangement (7, 9) is used to guide the beatpiece (64) within the rearward spindle part (40a).
  • the forward sleeve (7) is formed as a hollow cylinder and has a forward reduced internal diameter guiding portion (7a), which fits around and guides a forward reduced external diameter portion of the beatpiece (64).
  • the rearward sleeve (9) is also formed as a hollow cylinder and has a rearward reduced internal diameter guiding portion (9a), which fits around and guides a rearward reduced external diameter portion of the beatpiece (64).
  • the two guiding portions (7a, 9a) are widely axially spaced and so the axial guiding of the beatpiece (64), so that the beatpiece (64) reciprocates with its axis co-axial with the axis of the spindle (40a), is very accurate. This greatly improves the efficiency with which impacts are transmitted by the beatpiece from the ram (58) to the tool or bit (68).
  • the sleeves (7, 9) and the beatpiece (64) are dimensioned so that there is an annular gap between the outer surface of the increased external diameter portion (64a) of the beatpiece and the inner surface of the increased internal diameter portions of the sleeves (7, 9).
  • the beatpiece (64) reciprocates, grease is free to move between a region in front of the increased diameter portion (64a) and a region behind the increased diameter portion (64a) of the beatpiece.
  • reciprocation of the beatpiece (64) does not pump grease forwardly and rearwardly.
  • a ram catching sleeve (23) is located within the spindle part (40a) behind the rearward sleeve (9), partially surrounding the rearward end of the rearward sleeve (9).
  • the ram catching sleeve has a radially inwardly directed flange (63) formed at its rearward end the forward face of which is spaced from the rearward end (9a) of the rearward sleeve (9). In this space is located a resilient O-ring (17) for catching the ram in its idle mode position.
  • the front sleeve (7) has a mass, which is substantially the same as the mass of the beatpiece (64).
  • a slight axial play in the location of the sleeves (7, 9) within the spindle part (40a) enables a gap (13) to be created between a forward facing annular surface (7c) of the sleeve (7) and a rearwardly facing end face (41) of the forward spindle part (40b).
  • the gap (13) may or may not exist depending on the position of the forward sleeve (7).
  • the ram (58) moves into its forward position, in which it is caught in the ram catching O-ring (17).
  • the beatpiece (64) moves into its forwardmost position and the increase diameter portion (64a) of the beatpiece impacts a rearward facing internal shoulder (7d) of the forward sleeve (7), thus transferring its forward momentum to the front sleeve (7).
  • the reflected momentum from the sleeve (7) causes the beatpiece (64) to then move rearwardly, but not with a sufficient momentum for the beatpiece (64) to impact the ram (38) with sufficient force to dislodge the ram (58) from the ram catching O-ring (17).
  • the front sleeve (7) on being impacted by the beatpiece (64) moves forwardly to close the gap (13) and transfers its forward momentum to the rearward end face (41 ) of the spindle part (40b).
  • the reflected momentum from the spindle part (40b) causes the sleeve (7) to move rearwardly, but not with sufficient speed to catch up with the beatpiece (64).
  • the rearward momentum from the front sleeve (7) is transferred to the rear sleeve (9) and from the rear sleeve (9) to the spindle part (40a) via the damping ring (25), ram catching sleeve (23) and the snap ring (27).
  • the reflected momentum of the forward sleeve (7) is not transmitted to the beatpiece, which remains caught in its idle mode position by the ram (58).
  • the tool or bit (68) When a user wishes to use the hammer again, the tool or bit (68) is pressed against a working surface and so the tool or bit is urged rearwardly in the spindle part (40b) to urge the beatpiece (64) rearwardly, the beatpiece (64) urges the ram (58) rearwardly and out of the ram catcher (17) to close the vents and form a closed air cushion between the piston (38) and the ram (58).
  • the piston (38) when the user actuates the trigger switch (8) of the hammer the piston (38) is reciprocatingly driven in the spindle part (40a) and the ram (58) follows the reciprocation of the piston due to the closed air cushion and hammering occurs.
  • the rearward sleeve (9) acts to damp reflected impacts to the beatpiece (64) during operation of the hammer.
  • a resilient O-ring (25) is located between a radially outwardly directed flange (9c) of the rearward sleeve (9) and the forward end face of the ram catching sleeve (23).
  • the ram catching sleeve (23) is held against rearward movement within the spindle part (40a) by a snap ring (27).
  • the O-ring (25) damps the reflected impacts which are transmitted from the working surface, via the tool (68) to the beatpiece (64).
  • the beatpiece (64) transmits these impacts to the sleeve (9), which transmits the impacts via the damping ring (25), which damps the impacts, via the sleeve (23) and snap ring (27) to the spindle part (40a).
  • the two part sleeve arrangement (7, 9) has a seal (21) recessed within the forward end of the front sleeve (7) for sealing around the beatpiece (64).
  • the O-rings (25) and (29) act to form a seal between the exterior of the sleeves (7, 9) and the internal surface of the spindle part (40a). This seals around the beatpiece against dust entering the part of the spindle part (40a) behind the seals (21, 25, 29) and against grease leaving the part of the spindle behind the seals (21, 25, 29).
  • the seal (21) is located at the forward end of the sleeve arrangement (7, 9) the guiding of the beatpiece (64) using guiding portions (7a, 9a) is done within the grease filled region of the spindle part (40a). Furthermore, the sleeves (7, 9) and beatpiece (64) fill the space between the beatpiece (64) and the spindle part (40a) and so provide a physical barrier to the ingress of dust.
  • the sleeves (7, 9) are mounted within the spindle part (40a) with close tolerances between the radially outermost parts of the sleeves and the internal surface of the spindle. However, the sleeves (7, 9) are mounted so as to be able to have a limited axial movement within the spindle, as described above. Forward movement of the front sleeve (7) is limited by the rearward end face of the spindle part (40b). The forward end of the rearward sleeve (9) abuts the rearward end of the forward sleeve (7) and rearward movement of the rearward sleeve (9) is limited by the ram catching sleeve (23) and snap ring (27). It can be seen that the two part sleeve design described above and shown in Figure 3 facilitates easy assembly of the beatpiece (64), sleeves (7, 9) and other associated components from the rearward end within the forward spindle part (40a).
  • the arrangement in Figure 4 is similar to that shown in Figure 3, except that the spindle (40) is a single piece with a forward end having a stepped reduced diameter portion acting as a tool holder for a tool or bit (68). Therefore, the forward movement of the forward sleeve (7) is limited by a rearward facing internal shoulder (31 ) formed in the spindle (40).
  • the top half of Figure 4 shows the hammer components in their idle mode position, with the ram (58) caught in the ram catching O-ring (17).
  • the bottom half of Figure 4 shows the hammer components in their operating positions.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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Claims (19)

  1. Marteau mû électriquement, comprenant:
    une broche creuse (40, 40a, 40b) comportant au niveau de son extrémité avant une partie porte-outil de diamètre réduit (40, 40b), dans laquelle un outil ou un burin (68) peut être monté de façon amovible de manière à avoir un déplacement en va-et-vient limité, broche dans laquelle sont montés de manière à se déplacer en va-et-vient un piston (38) et un coulisseau (58) d'un mécanisme de marteau à air comprimé;
    un organe de frappe (64) possédant une partie médiane de diamètre extérieur accru (64a), située à l'intérieur de la broche entre le coulisseau (58) et l'outil ou un burin (58) pour une transmission d'impacts répétés par le coulisseau à l'outil ou au burin; et
    un agencement de manchon en deux parties (7, 9) situé à l'intérieur de la broche et possédant une partie médiane de diamètre intérieur accru servant à recevoir la partie de diamètre accru de l'organe de frappe et des parties avant et arrière de diamètre intérieur réduit pour guider respectivement les extrémités avant et arrière de l'organe de frappe (64) dans toutes les positions de travail de ce dernier,
       caractérisé en ce que l'agencement à manchons est formé par un manchon avant (7) et un manchon arrière (9), qui sont tous deux guidés avec des tolérances radiales serrées et avec un léger jeu axial à l'intérieur de et par la même partie de broche monobloc (40, 40a, 40b), et dans lequel le déplacement axial d'avance du manchon avant (7) est limité par une partie de diamètre réduit de là broche (40, 40b) et le déplacement axial d'avance du manchon arrière (9) est délimité par le manchon avant.
  2. Marteau selon la revendication 1, dans lequel un joint d'étanchéité annulaire (21) est situé en aval du manchon avant entre l'organe de frappe et ladite partie de broche monobloc (40, 40a).
  3. Marteau selon la revendication 1, dans lequel un joint d'étanchéité annulaire (22) est situé entre l'organe de frappe et l'extrémité avant du manchon avant (7).
  4. Marteau selon la revendication 3, dans lequel le joint d'étanchéité annulaire (21) est en renfoncement à l'intérieur de l'extrémité avant du manchon avant (7).
  5. Marteau selon l'une quelconque des revendications 2 à 4, dans lequel un joint d'étanchéité annulaire (29, 25, 11) est disposé entre le manchon avant (7) et ladite partie de broche monobloc (40, 40a).
  6. Marteau selon l'une quelconque des revendications précédentes, dans lequel l'agencement à manchons (7, 9) entoure la partie médiane de l'organe de frappe (64) pour former un sous-ensemble autonome, qui est assemblé dans ladite partie de broche monobloc (40, 40a).
  7. Marteau selon l'une quelconque des revendications précédentes, dans lequel la masse du manchon avant (7) est inférieure ou égale à la masse de l'organe de frappe.
  8. Marteau selon la revendication 7, dans lequel la masse du manchon avant (7) est inférieure à la masse de l'organe de frappe.
  9. Marteau selon l'une quelconque des revendications précédentes, dans lequel l'organe de frappe possède une seconde partie de diamètre extérieur accru (64b) située en arrière de la première partie et qui peut coopérer avec une bague élastique (15) de retenue de l'organe de frappe, laquelle bague est montée à l'intérieur du manchon arrière (9), pour retenir l'organe de frappe dans une position avant dans le mode de fonctionnement à vide.
  10. Marteau selon l'une quelconque des revendications précédentes, dans lequel un interstice annulaire est formé entre la surface périphérique des parties de diamètre accru (64a, 64b) de l'organe de frappe et une partie de diamètre intérieur accru de l'agencement à manchons (7, 9).
  11. Marteau selon l'une quelconque des revendications précédentes, dans lequel une bague métallique d'impact (48) de l'organe de frappe est montée dans le manchon arrière (9) en arrière d'une surface, tournée vers l'arrière, de la partie de diamètre accru (64a) de l'organe de frappe pour absorber des impacts inverses provenant de l'organe de frappe et transmettent les impacts au manchon arrière (9) pendant l'utilisation normale du marteau.
  12. Marteau selon la revendication 11, dans lequel une bague d'amortissement (15) est montée dans le manchon arrière (9) à l'arrière de la bague d'impact (48) pour amortir les impacts transmis par la bague d'impact au manchon arrière (9).
  13. Marteau selon la revendication 12, considérée comme dépendante de la revendication 9, dans lequel la bague d'amortissement de l'organe de frappe et la bague de retenue de l'organe de frappe sont formées par le même composant (15).
  14. Marteau selon l'une quelconque des revendications précédentes, dans lequel les impacts inverses dûs à l'organe de frappe (64) lors de l'utilisation normale du marteau sont transmis par la partie de diamètre accru (64) de l'organe de frappe à la broche par l'intermédiaire du manchon arrière (9).
  15. Marteau selon la revendication 14, dans lequel un joint torique élastique (25) est situé entre un épaulement extérieur, tourné vers l'arrière du manchon arrière (9), et un organe de fixation (23) servant à limiter axialement le déplacement arrière du manchon arrière à l'intérieur de ladite partie de broche monobloc (40, 40a) et pendant le fonctionnement normal du marteau, la partie de diamètre accru (64a) de l'organe de frappe vient en butée, de façon répétée, contre un épaulement intérieur, tourné vers l'avant, du manchon avant (9).
  16. Marteau selon l'une quelconque des revendications précédentes, dans lequel une bague torique élastique (11) situé entre un premier épaulement, tourné vers l'avant, du manchon avant (7) et le première épaulement, tourné vers l'arrière, de la broche (40, 40a) repousse le manchon avant dans une position arrière à l'intérieur de la broche de manière à ouvrir un interstice (13) entre une partie, tournée vers l'avant, du manchon avant (7) et une partie, tournée vers l'arrière, de la broche, lequel interstice (13) est fermé par le déplacement d'avance du manchon (7) lors du passage du marteau au mode de fonctionnement à vide.
  17. Marteau selon l'une quelconque des revendications précédentes, dans lequel la broche creuse (40) est agencée sous la forme d'un seul composant.
  18. Marteau selon l'une quelconque des revendications 1 à 16, dans lequel la broche est agencée sous la forme de deux composants (40a, 40b).
  19. Marteau selon la revendication 18, dans lequel le premier composant (40a) loge le piston, le coulisseau et l'organe de frappe, et un second composant (40a, 40b) forme un porte-outil, qui peut être retiré du premier composant.
EP02251438A 2001-03-07 2002-03-01 Marteau Expired - Lifetime EP1238759B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GBGB0105547.4A GB0105547D0 (en) 2001-03-07 2001-03-07 Tool holder for a rotary hammer or a chisel hammer
GB0105547 2001-03-07
GBGB0125749.2A GB0125749D0 (en) 2001-10-26 2001-10-26 Power tool
GB0125749 2001-10-26

Publications (2)

Publication Number Publication Date
EP1238759A1 EP1238759A1 (fr) 2002-09-11
EP1238759B1 true EP1238759B1 (fr) 2003-12-17

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US (2) US6732815B2 (fr)
EP (1) EP1238759B1 (fr)
JP (1) JP4195228B2 (fr)
CN (1) CN1257044C (fr)
AT (1) ATE256533T1 (fr)
DE (1) DE60200127T2 (fr)
ES (1) ES2208623T3 (fr)
PT (1) PT1238759E (fr)

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SE509211C2 (sv) 1994-02-28 1998-12-21 Berema Atlas Copco Ab Handhållet tryckluftdrivet maskinspett
JP2996277B2 (ja) 1994-06-15 1999-12-27 富士ゼロックス株式会社 画像形成装置
JP3424870B2 (ja) 1995-02-28 2003-07-07 株式会社マキタ 打撃工具の空打ち防止装置
JP3483015B2 (ja) 1995-10-16 2004-01-06 古河機械金属株式会社 油圧打撃装置の緩衝機構
JP3292972B2 (ja) 1996-03-29 2002-06-17 株式会社マキタ 打撃工具
DE19621610B4 (de) 1996-05-30 2016-06-23 Robert Bosch Gmbh Einrichtung zum Wechseln des Werkzeughalters an einer Handwerkzeugmaschine
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US5954140A (en) 1997-06-18 1999-09-21 Milwaukee Electric Tool Corporation Rotary hammer with improved pneumatic drive system
DE29711704U1 (de) 1997-07-04 1997-09-04 Hilti Ag, Schaan Bohr- und/oder Meißelgerät
US5896934A (en) 1997-09-08 1999-04-27 Chicago Pneumatic Tool Company Reciprocating tool having a piston retainer
JPH11104974A (ja) 1997-10-06 1999-04-20 Makita Corp 打撃工具
DE19810088C1 (de) 1998-03-10 1999-08-26 Bosch Gmbh Robert Bohr- und/oder Schlaghammer mit in Abhängigkeit von der Einstecktiefe eines Werkzeuges aktivierbarem Schlagwerk

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004195648A (ja) * 2002-12-19 2004-07-15 Hilti Ag 打撃駆動する電動手工具装置
JP4648624B2 (ja) * 2002-12-19 2011-03-09 ヒルティ アクチエンゲゼルシャフト 打撃駆動する電動手工具装置

Also Published As

Publication number Publication date
US6732815B2 (en) 2004-05-11
DE60200127D1 (de) 2004-01-29
CN1374172A (zh) 2002-10-16
JP4195228B2 (ja) 2008-12-10
US20040194987A1 (en) 2004-10-07
US20020125023A1 (en) 2002-09-12
JP2002321169A (ja) 2002-11-05
PT1238759E (pt) 2004-04-30
EP1238759A1 (fr) 2002-09-11
CN1257044C (zh) 2006-05-24
DE60200127T2 (de) 2004-06-03
ES2208623T3 (es) 2004-06-16
US6948571B2 (en) 2005-09-27
ATE256533T1 (de) 2004-01-15

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